Truck loader



Feb. 12, 1946. R. c. SHOEMAKER TRUCK LOADER Filed Dec. 14,V 1942 l 6 Sheets-Sheet 1 BV QM,

Feb' 12 1.946- I R. c. sHoEMAKER 2,394,940

r TRUCK LOADER 6 Sheets-Sheet 2 Filed Dep. 14, 1942 1 Feb. 12, 1946. R. c. sHoEMAKER TRUCK LOADER Filed Dec. 14, 1942 G Sheets-Sheet 5 Feb. 12, 1946. R. c. SHCI-:MAKER TRUCK LOADER Filed Dec. 14, 1942 e sheets-sheet 4 771 l lllrfa y (mj nllilugg 65 1 y Lz/JQ.-

EEEEEEEEEEEE Feb. 12, 1946. K R Q SHOEMAK-ER 2,394,940-

" TRUCK LOADER Filed Deo. 14, 1942 6 Sheets-Sheet 5 Feb.1!2, 1946. R. c, sHoEMAKER TRUCK LOADER Filed Dec. 14, 1942 e sheets-sheet s Patented Feb. l2, 1946 TRUCK LOADER Robert C. Shoemaker, Portland, Oreg., assigner to Willamette -Hyster Company, Portland, Oreg., acorporation of Oregon ApplicationDecember 14, 1942, Serial No.` 468,927

2s claims.

This invention relates to improved truck loading apparatus, and more particularly to such ap paratus which is transportably mounted upon and is operated by movement of the truck, or to be more explicit, it is operated by the forward and reverse rotations of one of the Wheels of the truck.

Such apparatus may be installed as a component of a truck at the factory, but conveniently takes the form of a 'unitary attachment-designed to be mounted by or forv the user upon an existing truck. The apparatus includes a supporting structure; a material handling device such as a slip scraper bucket, rockfork, cradle or the like; means for actuating the material handling device to move back and forth between material Aengaging or receiving and truck loading positions; and means connected up with a wheel of movement of the truck may be utilized to deliver the bucket into material-engaging position at the side of the. truck and also to drag the an improved truck mounted derrick-typeloader fin which the swinging axis of the hoisting boom is adjustable to compensate for undesirable unbalancing of the boom dueto tilting of the truck, and, optionally, to predispose the boomto swing in given direction.

Another object of the invention 4is to provide l an improved drag bar structure for -use witha truck having mounted thereon 4a loader embody bucket forwardly for scraping up a fill of the material while rearward movement of the truck is utilized to effect raising up and swinging of the bucket into a position over the truck body where A the material may b'e loaded into the truck by dumping the bucket.

One of the principal objects of my invention is to improve the construction and operation of truck loading apparatus of this character, with particular regard to improvements in the means for actuating and controlling operation of the load handling device of the apparatus.

Another object is to provide an improved loadn ing apparatus having a plurality of 'actuating cables arranged for operation. in a n ovel manner for effecting sequential and coordinated vertical and horizontal movement of theload handling.

device of the apparatus. l V l Another object is toprovide an improved wheelmounted, independently rotatable cable windingAVV drum structure and novel means for 'releasably connecting the drum structure for` rotation with the wheel. I

Still another object is to provide safety means yof the slip scraper bucket; Fig'. 10 is an enlarged vertical sectional detail view takensubstantially in the plane ofl line lll-I0 ofFig. 3 to showv detailsofthe mast and swivel mounting structures for the boom;

Fig. y11 is a horizontal sectional plan view taken yslip scraper bucket type of material handling dethroughout the several-views.

In the drawings: Figure 1 is afragmentaryand more or less schematic view of a small size standard dump ing the features of my invention;

Fig.`2 isa similar view on a reduced scale ,showing'various operative positions of the loader;-

Fig. 3l is a top plan view of the loader;

Fig. 4is an enlarged fragmental vertical sec-v of Fig. 3 showing details of the safety release' counterweight construction for the'swing cable slack take-up;

Fig. 5..is a front elevational view of the safety release vcounterweight structure partially broken away and in section for clarity of detail;

Fig. 6 is a horizontal sectional detail view taken substantially in the plane ofA line 6 6 of Fig. 4; Fig. rItis a rear elevational view taken'substantially from the position of line 'l-l of Fig. 1, looking forwardlyv toward the truck-mounted parts' of the loader;

' Fig. 8vv is an enlarged fragmentary elevational view of the rear sideV of the hoisting boom showing the' manner lin vwhich the adjustable stayl 'chain is connected therewith;

- Fig. 9v is a verticalsectional view taken in sub.- stantially the plane of line 9 -8 of Fig. 3 showing, on an enlarged scale,l details of the tripl 'latch mechanism' and quick detachable cable connector substantially in the plane of'line of Fig. 10;

Fig. 12 is a fragmentary vertical sectional view taken substantially in the plane of line I 2I 2 of Fig. 11 showing details of the boom latch;

Fig. 13 is a vertical sectional detail view taken in the plane of line |3-I3 of Fig. 12;

Fig. 14 is an enlarged fragmental vertical sectionaldetail view, taken substantially along the line |`4l4 of Fig. 11, showing the boom tilting adjuster;

Fig. 15 is a kvertical diametrical sectional view through the winding drum structure, taken substantially in the plane of line 5 of Fig. 16

Fig. 16 is a vertical sectional view through the winding drum structure, taken substantially along lines |8|6 of Fig. 15;

Fig. 17 is a. horizontal fragmentary detail sectional view, taken substantially in the plane of line |1|1 of Fig. 15 and showing the clutchhandle keeper plate;

Fig. 18 is a perspective view of an optional rock fork which is adapted to be used with the loader; and

Fig. 19 is an enlarged sectional detail view taken along line |9-|9 of Fig. 18, showing the mounting of one of the tines of the rock fork.

By way of illustration, the features of the invention are shown in the drawings as embodied in a truck loader, generally identified by the numeral 25, of a substantially self-contained unitary construction which is arranged to be removably mounted upon a dump truck 26. In the present instance the truck 26 is of the type which may be employed by highway maintenance crews, including a rearwardly tiltable open top dump body 21 located to a large extent above the rear driving wheels. Merely one of the rear wheels, at the right side of the truck, is shown and identified generally by the numeral 28.

The loader 25 is equipped to receive material at ground level and hoist it up into the truck body 21, being here shown (Figs. 1, 2 and 3) as espe-- cially adapted for digging or scraping out roadside ditches, such as that indicated at 29. For this purpose the loader has a slip scraper bucket 30 which is adapted to be dragged along the ditch under the guidance of a scraper attendant to dislodge and gather up material to be cleaned out oi.' the ditch 29 and loaded into the truck body 21.

Forward motion of the truck 26 is utilized for dragging the bucket 30 along within the ditch 29 to cause it to gather a load of material. For this purpose a drag line cable 3|- has a forked tail secured to the respective opposite sides of the mouth of the bucket 30 and has its forward end connected to the outer end of a drag bar 32. As best seen in Figs. 1, 3 and 7, the drag bar 32 comprises an elongated, reenforced angle bar frame of preferably triangular or A-shape which extends laterally at a downwardly slanting angle from the forward end of the truck body 21 with the pointed end of the frame as low as practicable to minimize the upward component of pulling force when dragging the bucket. At its upper, wider end the drag bar 32 has its legs pivotally secured to the inside faces or opposing backs of horizontally spaced, coextensively parallel front and rear mounting frame bars 33 and 34, respectively, of preferably channel shape, whch lie transversely of the truck body and have their ends projecting to a predetermined extent beyond the opposite sides of the truck body.

While it is generally desirable to have the outer end of the drag bar 32 as low as practicable in order to minimize the angle between the drag line 3| and the ground during a scraping operation, it nevertheless may be desirable from time to time to vary the elevation of the lower end or at least vary the distance to which such end extends from the side of the truck to accommodate various operational circumstances, `as may be done by adjustably swinging the bar about its pivotal axis. Means for holding the drag bar 32 in various swingably adjusted positions comprises a tie rod 35 having its lower extremity directed angularly forwardly to serve as a bearing pin 31 which is pivotally connected into an eye 38 at the point end of the drag bar frame. At its upper end, the tie rod 35 is formed with a rearwardly extending angular anchoring pin leg 39 arranged to be inserted through any selected one of a vertical series of graduated adjustment-determining holes 40'within the outwardly projecting flange of an angle iron outerstrut 4| associated with a mast 42. A displacement-preventing cotter pin 39a may be removably inserted through a suitable aperture extending transversely through the outer end of the anchoring leg 39. By removing the cotter pin 39a and disconnecting the anchoring leg 39, the drag bar 32 may be allowed to hang vertically out of the way at the side of the truck so as to avoid impedingtravel of the truck 2E while in transit from place to place. In such event, the tie rod 35 may be collapsed against the .drag bar and there held in place by a spring retaining clip 43, as indicatedl in dot-dash outline in Fig. 7.

Adjacent to the lower bearing pin 31, the tie rod 35 is formed with relatively shallow crook 44 adapted to form a seat for a shackle ring 45 of a quickly separable coupling 46 by which the drag line 3| is connected to the drag bar structure. The shackle ring 45 is adapted to move slidably up along the tie rod 35 under certain conditions as will be more fully explained hereinafter.

The mounting frame bars 33 and 34 are secured together by preferably angle iron cross members 41 and 48 respectively adjacent to the left and right ends of the frame. The cross angles 41, 48 serve as runners (Figs. 3 and 7) which are appropriately spaced to rest .upon the upper side edge beads of the truck body 21 to which the runners are removably secured by means such as J-bolts 49.

In order to receive removable side boards 50 forming side wall upward extensions for the body 21, vertically extending, rearwardly opening channel shaped sockets 5| may be mounted upon the rear frame bar 34 over the rear ends of the runners 41 and 48.

The mast 42 forms a component of a derrick structure through the medium of which the lled scraper bucket 30 may be raised into a position over the truck body 21 for loading thereinto of the bucket contents. In the present instance, the mast 42 comprises a tubular post which is adapted to be supported in a rigid vertical position by, in addition, to the strut 4|, an opposite or inner strut 52 and a rear strut 53, arranged pyramidally to converge at the top of the mast. Attheir upper ends, the mast 42 and the struts 4|, 52 and 53' are fixedly secured to a horizontal crown plate 54. At their lower ends the mast 42 and the struts are rigidly secured to a base frame 55. The entire mast, strut and base frame structure is preferably welded into a solid unit, which is exceedingly strong, compact and light in mit freely slidable reception at the inside faces weight.

As bestseen in Figs. and 11, the base frame 55 preferably comprises a rectangular arrangement adapted to be received between the mounting frame bars 33 and 34. It comprises coextensive, parallel front and rear side bar strips 51 and 58 extending longitudinally along and closely broadside to the frame bars 33 and 34, respectively, and secured into a rigid unit adjacent to their` left and right endsA by reenforcing channel cross bars 59 and 60, respectively. These cross bars support the respective side struts 52 and 4I. Centrally of the base frame, extending frame bars 33 and 34, supporting pins or shafts f 63 and 64 extend slidably through suitable apertures adjacent to the left and right ends, respectively, of the side frame bars 51, 58, and at their ends project out through coaxial pairs of shaft holes 65 formed in the respective vvebs of the mounting frame bars 33 and 34. The shaft holes 65 are preferably provided in uniform series throughout the length of the mounting frame bars 33' and 34 so that the base frame 55 may be mounted at any of a plurality of selective positions along the mounting frame as required for various practical conditions. Thus, the base frame 55 is adapted-to be mounted at the right side of the truck, as shown herein, since the derrick and scraper are to be used. at that side of the truck, or the entire arrangement may conveniently be reversed for use at the left side of the truck. Moreover, this arrangement also permits the loader to be used with trucks of various optional widths or under conditions requiring the derrick to be located inwardly from either side of the truck rather than directly over one of thegsides as shown. Longitudinal displacement of the mounting shafts 63 and 64 is restrained by means such as cotter pins 66.

By removing one of the cotter pins 66 from the supporting shaft 64, the shaft may be withdrawn and the mast tipped over into an inactive horizontal position by pivoting it on the supporting shaft 63, as may become necessary, due t-o low headroom, in order to permit the truck to pass through a garage door or a shallow underpass, or the like.

A boom 61 is supported for swinging movement about the vertical axis of the mast 42. In the present instance the boom 61 comprises a tapering tubular structure of rectangular crosssection, thus embodying great strength with a minimum of weight. At its base or heel the boom 61 is mounted upon a swivel member herein comprising a bull wheel 68. As best seen in Figs. 3, 10 and l1, the bull wheel 68 is rotatably mounted coaxial with the base of the mast,42. Rigid upon the upper surface of the bull wheel is a pair of identical elongated boom 'mounting flanges 69 in the form of identical parallel plates secured in place as by welding along oneA longitudinal edge on equally spaced opposite chords of the bull wheel, the spacing being such as to perof the iianges of depending heel lugs 10 formed as integral parallel extensions of the sides of the boom 61. A heel pin 1I extends through the heel lugs 10 and projects at its opposite end through coaxial apertures 12 adjacent to the ends of mounting flange plates 69. It will be observed that the plates 69 are formed with apertures 12 adjacent to both ends so that the boom may be mounted selectively at either opposite side of the bull wheel. Cotter pins 13 may be utilized to hold the boom pin 1I against longitudinal displacement.

The boom 61 is preferably substantially longer by a third, more or less, than the height of the mast 42 and has its upper end portion formed to extend angularly outwardlyfrom the main body to form an overhanging head 14. Just below the shoulder where the head 14 meets the body of the boom 61, a tie member comprising a ch'ain 15 engages the boom to hold itin a preferred tilted relation to the mast 42. inner or back face of the boom is formed with a bayonet type of slot 11 (Fig. 8) having the larger opening thereof at the top and of suiiicient width to enable passage of the horizontally Wall at each side of Athe narrow portion of the slot. Any excess chain will hang down enclosed within the boom.

At its opposite end, the boom tie chain 15 is detachably anchored to a horizontal plate 18, which is slidably swiveled upon the head plate 54 by means of a rigid stud bolt or pin 19 coaxial with the mast 42. A castle nutA 80 threaded on the pin 19 bears against a h'old down ywasher 8| lying on the anchor plate. Through this arrangement the boom 61 is held at the preferred degree of angularity relative to the mast 42, and the angularity may be adjusted by adjusting the chain 15 in th'e bayonet slot-11. Where, for example, the boom head 14, due to its height, will not pass under an overhead obstruction, which will, however, admit the mast 42, the boom may be dipped until the uppermost point of the h'ead 14 attains the level of the top of the mast (see broken outline position of Figs. 1 and 7), being tied in this position by appropriate interlocking of the chain 15 in the slot 11.

At the tip of the boom head 1-4 is a shackle 1aa v swingably suspending a fairlead pulley block 82 for a hoist line cable 84 by which the scraper bucket 30 is adapted to be raised above the truck body 21. The arrangement is preferably such that the boom will extend outwardly and rearwardly at an angle of approximately 45 relative to the side of `the truck into an overside hoisting or pickup position (Figs. 1 and 3) wherein the fairlead block 82 is over substantially the -longi- For -vthis purpose the body which may be formed from cast steel and is preferably pivotally attached to the bucket.

' A lug or ferrule 81 is securely fastened to the end of the hoist line 84 and provides :i head of somewhat smaller diameter than the body 85 but of substantially larger diameter than the hoist line.l The head 81 is adapted to be received through an openingwhich will just clear it in one side of the body 85 for entrance into a socket chamber 88. Assembly of the head 81'within the socket charnber 88 is effected by relative lateral assembly movement of the body and head, the adjacent portion of the hoist line 84 being received within an appropriate slot 89 in the top of the body 85.

Then by relative opposite longitudinal movement of the hoist line 84 and body 85, the head 81 is caused to lodge in a socket recess in tha chamber 88 above the top edge of the entrance opening. The head 8 1 will remain in the socket recess until the hoist line 84 is slackened suiliciently to permit intentional withdrawal of the head.\ Thus, when there is even a slight tension on the hoist line 84, the head 81 will be held thereby against separation from the body 85 and should the hoist line fall slack when the bucket 30 is at rest, the socket body may tip over so that thev head 81 is held in its socket by gravity whereby to maintain the connection. However, an intentional separation can be easily and quickly effected as desired. This is of particular value where, after the truck has been loaded and must be driven to a place selected for dumping the load, the scraper bucket 38 can be quickly disengaged from the hoist line 84 and left at the site of the scraping operation until tne empty truck returns to resume the scraping and loading. To this end, the quick separable coupling 45 for the drag line 3| may be of identical construction as the hoist line coupling 85, 81, just referred to.

Th'e socket body 85 of the hoist line coupling is preferably secured over substantially the center of gravity of the bucket 38 in such a manner that the filled bucket can be readily tipped for discharging its contents into the truck body 21. For this purpose, trip mechanism 90 (Figs. 1, 3 and 9) is provided in association with the hoist line coupling for normally holding the bucket horizontal when A hoisted, but permitting the bucketto be released at a sufcient height to afford effective .loading clearance for the bucket. The retainer 9| extends substantially rearwardly from the center of gravity and to a lesser extent forwardly therefrom and has normally positioned therein a trip bar 94 which is only slightly shorter and has its rear end pivotally secured as at 95 between the upright flanges of the retainer in such manner as to enable approximately 180 swinging movement of the bar. An upstanding rigid attachment ear 96 on the trip bar 94 affords an anchorage for the coupler socket 85. The ear 96 may be elongated longitudinally of the trip arm and formed with' a longitudinal series of coupler pinholes 91 for selective attachment of the coupler 85 with respect to the center of gravity of the bucket.

At its forward end, the trip arm 94 carries an anti-friction roller 98 which is normally adapted to be engaged by a latch finger 99 carried for swinging movement into` and out of latching engagement by a rock shaft |08. An upstanding pair of spaced parallel supporting ears |8| at the forward end of the retainer 9| provide bearings for the shaft |80. Normally latching engagement of the latch nger 99 with the roller 98 is maintained by a torsion spring |02 which is coiled about the rock shaft |80 and has a leg |83 (Fig. 3) anchored in one of the ears |8| while a leg |04 at the opposite end of the spring bears against the forward face of the latch 99 to urge it normally rearwardly into position for engaging the trip bar roller 498. An upwardly extending release finger |85 is rigidly associated with the latch finger 99, engageable with a stop |81, which limits the inward tilting movement of the latch 99 under the influence of the spring |82.

A trip line |08 is secured at one end to the l upper end of the trip nger |05 and leads back Vthrough an upstanding guide loop |89 at the rear of the retainer 9| for convenient manipulation by the bucket attendant who may pull it at will for swinging the latch 99 against the action of the torsion spring |82 and thus releasing the trip bar 94. The weight of the bucket 30 and contents thereupon causes the trip bar 94 to swing down at its rear end and up at its forward end about the hoist line coupling pivot, and the bucket to swing down about the offcenter pivot 95 with the bucket mouth hanging down to discharge its contents, substantially as seen in the left hand dot-dash position of Fig. 2.

To reset the trip mechanism 98 after the bucket has been returned to scraping position, the trip bar 94 is jackknifed back into the retainer 9| whereby the roller 98 rides against the latch 99, clearing the latch from its path and then allowing it to snap into latching position when the arm has fully returned into the retainer.

Means is provided for automatically operating the hoist line cable 84 in response to movements of the truck 26 not only for hoisting the scraper bucket 38 to loading height above the truck body v21, but also for returning the bucket to the scraping and material-gathering position at ground level beside the truck. Herein such means comprises a peripherally flanged or grooved reel or winding drum ||8 mounted coaxially upon the rear truck wheel 28. ing end of the hoist cable 84 is secured to the winding drum ||8 by extending it through a radial opening I|| in thel drum periphery (Fig. 16) equipped with an easement piece ||2 within which the cable end is secured by means of a cable clamp ||3.

In the present instance, the cooperative association of the drum ||8 with the wheel 2B is such that in the forward rotation of the wheel 28 the drum may follow and the hoist line cable 84 be payed out, while in the reverse or backing up rotation ofthe wheel the drum may also follow and reel the cable in. After the cable is fully payed out, forward rotation of the wheel may continue independently of the drum while the bucket 38 is dragged forward to scrape up a load of material.

The circumferential dimension of the drum I8 is so correlated.V with the effective l gth of the hoist cable 84, that as the cable is/reeled in upon backing up of the truck after a scraping run, all slack is gradually taken up until the fairlead pulley 82 and the boom head 14 come into vertical position over the bucket 38 where it has come to rest (see the intermediate dot-dash position of Fig. 2). Then in the continued reverse movement of the truck and reeling in of the hoist line The pulli 3 4, guides bucket can be moved into the desired loadingV position to be unlatched for discharging its contents into the truck (see left-hand broken line position of Fig. 2 and broken line position of Fig. 3). Thereafter the empty bucket is returnable to the ground level scraping position, by swinging of the boom 61 back to the overside position and driving of the truck forwardly to pay out the hoisting cable 84. Since, `in returning the bucket 30, the same amount of hoist cable is payed out as wasnreeled in for-hoisting it, the bucket will return to substantially the same spot from which it was raised, as the truck moves forwardly in the same'path. As a result, scraping of the ditch 29 will progress continuously and without a. gap even though periodically interrupted by loading of the scraped up bucket contents into the truck.

In the hoisting and swinging of the bucket 30 over the truck body 21, complete freedom from any retarding influence by the relatively short drag line 3| is assured by sliding of the shackle ring 45 up the tie rod 35, as indicated in the lefthand broken line position of Fig. 2.

A guide pulley in a tackle block H4, pivotally anchored to a rigid upstanding ear ||4a at the adjacent outer end of the mounting frame bar the hoisting cable 84 substantially straight onto or off of the winding drum H despite the relatively wide swing executed by the boom head 14 and the block 82 in the course of operation. v

In orderyto space the winding drum H0 sufficiently axially from the wheels to afford adequate clearance for the windup reach of-the cable 84 beyond the edge of a wheel fender where present,

ora tool bo): carried by the truck, or other laterallyv 'projecting part, the drum is preferably mounted upon a substantially cupshaped extension flange structure H (Figs. 3, 7 and 15) which is removably secured as by means of cap screws H1 to an adapter flange structure H8. The latter, in turn, may be removably bolted to the hub of the wheel 28 by the lug bolts (not shown) of the wheel. This arrangement facilitates mounting and dismounting of the winding.

order to enclosema relatively protected mechanism chamber |28 in the space between the flange base and the body plate. Spokes |29 support the drum H0 in rigid concentrically spaced relation to the'innerclosure drum |21. Through thiskarrangement, the extension flange H5 at all times rotates with the wheel za while the drum nu is t adapted by the bearing for independent rotation, or, to put it another way, is rotatably independent of the extension flange and wheel.

l Optional interconnection of the drum H0 and the extension flange H5 to effect rotation of the winding drum with the' wheel, in this instancein response to reverserotation of the wheel, while preserving the rotativeindependence of the wind-A ing drum inthe opposite rotation of the wheel, is attained through the medium l of a one-way clutch arrangement such as a pawl |30 engageable with a peripherally toothed ratchet ring |3| the body plate |26within the chamber |28 upon a fixed pivot pin |32 which may be secured to (Figs. 15 and 16).r The paWl |30 is mounted upon the inside face ofy the plate |26 as by having a reduced diameter threaded end |33 extending out'v through the' body plate preferably adjacent the normally uppermost point thereof andfsecured in plate by a nut |34. A leaf spring |35 carried by the pawl bears against-, the adjacent inner vface of the closure drum |21 and normally urges the i .paWl |30 toward the toothed periphery of the The latter is mounted for nor-v mal rotation with the wheel 28 by being secured to ratchet ring |3|.

the extension flange I I5.

By preference,y the mounting of the ratchet ring |3| includes anl overrun safety release structure which inemergency `yvill permit the ratchet ring drum. When desired, the drum structure may, y

the extension flange H5 is a spindle or axle H0 upon which is removably mounted a ball bearing |20 held in place thereon by a snap ring |2| fitting in a peripheral groove |22 in the forward end portion of the axle. Fitted onto and rotatable with the outer race of the bearing |20, is an annular housing block |23 to which the drum H0 is adapted to be removably secured through the medium of cap screws |24 extending through the overlapping margins of a hub-hole closure plate |25 and a radial body disk'plate |26. These plates may be secured together permanently as by welding. The diameter ofthe body plate |26 is substantially less than the inner diameter of the drum H0 proper, but is greater than the diameter of the extension ilange||5 and carries about its edge an inwardly extending .cylindrical flange or inner closure drum |21 which is of sufficient width to overlap the edge of the base of the extension flange in slightly spaced relation in to have a relative rotative movement opposite to that of the supporting vehicle wheel. Accordingly, the ratchet ring is internally dimensioned to fit in spaced concentric relation about the bearing housing |23 near the body plate |26 and is formed with a concentric reduced diameter inner radial shoulder |31 which is turned to a running fit with the inner edge of anannular angle |38 kflxedly secured as by cap screws |39 to the base of the extension flange H5. Interposed between the adjacentface of the angle |30 and the'facc of the ratchettring |3| is 'a friction ringA |40. Bearing against the directly opposite face of the angle |38 is a similarfriction ring |4|. A clamping ring |42 bears against the friction ring |4I and is drawn up tight toward the ratchet ring by such means as follow cap screws |43 to place the interposed friction rings and angle flange under selectively adjustable compression. Ihis provides a constant=.,frlction clutch which is auxiliary to the pawl-ratchetclutch. The heads of thev screws |43 arepreferably countersunk within the outer face of the ratchet ring |3| and are accessible by a hexagonalk wrench through one or more coaxial wrench holes' |44 inthe body plate |26. The clamping ring |42 may be slightly dlshed on its clamping face so as to exenta somewhat flexible pressure when-'drawn tight. 1

v As a result of this arrangement, the vratchet ring |3| is normally held quite firmly for tion with the associated wheel of the vehicle. Should there be any extraordinary resistance to turning of the winding drum H0 when clutched for joint rotation with the vehicle wheel, the torsionin the ratchet ring |3| may overcome thev rotal might be called into play by accidental over-run-` ning of the truck after the hoisting cable 84 is wound to the limit upon the drum I0, thus developing an excessive tension which must be relieved, or by accidental over-accelerated backing up of the truck, eilecting a sudden jarring engagement of a tooth of the ratchet ring with the pawl |30. However, the latter condition will ordinarily never be very pronounced,'because, as

voi.' a neutral position. As seen in Figs. 15 and 17,

the pawl |30 is shown in full line in the active or clutching position and in broken outline in the neutral position, wherein the pawl has been shifted adjacent to the end of the pivot pin |32 out of-engagement with the ratchet ring I 3 I. For this purpose, the friction clutch angle |38 affords a neutral space to receive the pawl |30.

Shifting of the pawl 30 between the active and inactive positions is effected manually through the medium of a, xedly associated handle rod |45 which projects out through the closure drum |31 through a clearance aperture |41 between a pair of the spokes |29. A keeper plate |48 is removably and reversibly secured over the aperture |41 by means of cap screws |49 and has a substantially U-shaped slot |50 (Fig. 17) through which the handle |45 projects. 'I'he legs of the keeper slot |50 extend in the direction of the normal rocking of the handle |45 under the iniiuence of the leaf spring |35 working against the pawl, and are spaced'apart for respectively retaining the handle |45 against displacement longitudinally of the pivot pin |32 out of either of the optional active or inactive positions of the pawl. In order to effect a shifting of the pawl, the handle |45 may be digitally engaged and rocked in opposition to the tension of the if desired, in any degree of windup and the truck driven forwardly, the clutch in such case preferably being neutralized yto save it from wear. One way in which the drum can be thus held is by locking the cables against unwinding by means of any appropriate clamping or tying means secured through the spokes |29 and over the wound cables within the reel-channel of the drum.

Automatic means coordinated in operation with the hoisting cable 84 is provided for swinging the boom 81 into loading position over the truck body 21 as the bucket 30 is hoisted. Herein such means comprises a swing line such as a cable |5| (Figs. 1, 3 and 7) which, adjacent to one end, is secured either directly to the boom 61 (as shown in full outline in all views) or within the grooved periphery of the bull wheel 68 (dot-dash outline position of Figs. 3 and 7).

Where the swing line is secured directly to the boom 61, it is preferably engaged by a cable clamp |52 carried by a link plate |53 which pivotally engages a ilxed shackle |54 mounted approximately two-thirds of the way up the fairlead side of the boom. Initially the swing line cable |5| may be longer than required for Wear replacement, and the reserve length of cable is inserted through an opening |55 in the adjacent wall of the hollow boom to hang out of the way within the interior.

From the boom, the swing line cable |5| ex tends to substantially the opposite end of the mounting frame of the loader unit, where it passes over a pulley in a tackle block |51 which is anchored to a fixed upstanding ear |58 on the front mounting frame bar 33. Thence the swing cable extends back toward and beyond the derrick end of the mounting frame through the pul- ,ley of a lead block |59 pivotally anchored to an upstanding rigid ear |60 on that end of the mounting frame bar 33.

leal.' spring |35 to clear the slot leg in which it happens tovbe engaged, whereafter the handle is pushed through the lateral connecting portion of the keeper slot |50 and allowed to snap into place in the remaining leg of the slot. The length of the clutch-in leg of the keeper slot is, of course, suillcient for free rocking of the handle |45 without dislodgment as the pawl |30'rides over the respective teeth of the ratchet ring |3I. The neutral leg of the slot is preferably shorter whereby to holdV the neutralized pawl out of contact with the shoulder of the angle |38 and avoid possibly damaging friction in transit.

Thus it will be lseen that the winding drum may be quickly clutched or'declutched. When clutched, the pawl |30 and the ratchet ring |3| interengage upon slight reverse movement of the wheel 28 for effecting joint' rotation of the wheel and the winding drum ||0. Upon forward rotation of the wheel, the drum |0 may rotate jointly therewith until the cables are unwound,'the pawl and ratchet wheel being held interengaged by the tension of the cables. As soon as the cables are -fully unwound, the winding drum is held substantially stationary by the cables while the wheel continues forward rotation, and the pawl slides freely over the ratchet teeth. It will be apparent,

Herein it is contemplated that the winding drum ||0 also serve to actuate the swing cable 5|, and for this purpose the pull end of the swing cable is secured to the drum by means of@ the cable clamp ||3 (Fig. 16). Engagement by the clamp is preferably eilected close to the extremity of the cable so that as the adjacent stretch of the cable shows Wear due to flexure and windings, the worn part may be cut off and replaced by the next succeeding stretch by drawing upon the reserve provided at the boom end of the cable. l

Sinceit is necessary that the scraper bucket 30 be hoisted up for ample clearance of the side of the truck body 21 before the boom 61 is` swung toward the truck loading position, the relationship has been so devised that in thel wind-up rotation of the drum 0 the cable |5| will remain slack or at least exert no boom swinging pull until the hoisting cable 84 has been suillciently wound onto the drum to accomplish the prelim- 1 inary hoisting of the bucket. To this end, the

of course,- that the winding drum l0 may be held, 75

two cables engage the drum tangentially at diametrically opposite sides, with the hoisting cable on that side (herein the top) 'of the drum where the wind-up rotation oi' the drum (counterclockwise as seen in Fig, 16) will be instantly eiective to reel in the hoisting cable 84. On the other hand, the swing cable |5| approaches the drum tangentially in the same direction as the hoist cable but on the diametrically opposite side of the drum. The anchoring aperture and the cable clamp ||3 are located at approximatelyy the tangential meeting of the swing cable 5| and the drum l I0 so that the swing cable will actually be Since for practical reasons the diameter of the winding drum must be relatively limited, the half revolution lag in operation of the swingI line II may not afford suilicient differential to permit ample raising of the bucket 30 before the boom 61 is caused to swing. Means is therefore provided for appropriately prolonging the lag by increasing the differential in the cables. Such means herein comprises a take-up pulley within a tackle block |6I (Figs. 1, 3 and 10) overwhich the swing cable |5| is slack loopedintermediatg the blocks |51 and |59. A flexible take-up element such as a heavy cord or cable |62 supports the block |61 and 'is trained over a pulley |63 mounted for rotation about a. horizontal axis on a shaft |64 (Fig. 4) supported in centered relation adjacent to the upper end of the forward derrick strut 53.

A counterweight |65 secured to the take-up cable |62 is slidable up and down along the front of the strut 53 and is held against lateral displacement therefrom by'such means as spaced parallel wing plates |61 (Fig. 6)y which project therefrom at opposite sides o-f the strut and carry removable retaining pins |68 at the rear ofthe strut. The counterweight |65 acts normally to pull the tackle block I6I up and thus take up any slack that may tend to be present in the swingl line I5I, including such slack as develops during the first quarter initial wind-up revolution of the winding drum I I 0. Then in the second quarter of. the initial wind-up revolution the first vquarter slack off is reeled in. As the winding' drum continues reeling in, the normal slack iloop in the swing line is taken in to an extent predetermined by a limiting stop member I 69 (Figs. 6 and l0) which is engaged by and stops the counterweight |65 after predetermined slack take-up and arrests further paying out of the takeup cable |62 (broken outline position of Fig. 10). The stop member I 69 may be a bolt selectivelysecured in any one of a vertical series of stop bolt holes |10 formed in the web of the front strut 53.

Up to-the time that the counterweight |65 is halted by the stop bolt I 69, the boom 61 is held by i ciently to permit pulling up of the counterweight |65 in response to the reeling in of the swing line, Thereupon the .increased tension overcomes the trip latch |1| and releases the bull wheel 68 for rotation. Continued reeling in of the swing line I5I then results in swinging of the boom 61 into loading position over the truck body 21 (broken outline position at the left of Fig. 2 and in Fig. 3).

Having particular reference to Figs. 11, 12 and 13, the boom latch |1| in the present instance comprises a latch dog I 12 adapted to engage latchingly within an aperture I 13 appropriately located adjacent to the rim of the bull wheel 68. The dog. |12 is formed as an integral downward heel extension of a bell crank trip lever |14 which is pivotally vmounted for vertical rocking movement upon a short horizontal stud shaft |15 adjacent the end of the horizontally extending leg. An angular bracket |11 is mounted upon the spaced center frame bars 6| and overlies the margin of the bull wheel 68 for supporting the stud shaft |15. The remaining, vertical leg of the trip lever |14 extends upwardly and is formed with a bifurcation or pulley yoke |18 within which is rotatably mounted a guide sheave |19 under which the swing cable |5I is-trained.

By virtue of having the latch pulley |19 as nearly as lpracticable directly under the slack v takeup pulley I6I, a pull exerted upon the swing cable `I 5| while it is being reeled onto the winding drum IIO, is substantially directly effective in tending to rock the trip lever |14 upwardly for releasing the latch dog, |12. However, in order to restrain such rocking of the trip lever |14 until all of the differential slack in the swing line |5| has been reeled in by the winding drum.' a tension spring |80 is secured at one end to an outstanding y integral ear |8| adjacent to the upper'end of-,the vertical sheave yoke |18 and at its oppositey end Ato xed cantilever |82 on the supporting bracket ltion to the limit of the differential slack takeup.

Thereupon the spring |80 yields under the increased tension and consequent upward pull by the swing line, and the latch dog 12 leaves the latching aperture |13. Upward rocking of the trip lever |14 is limited by a fixed horizontal limit pin |83 which extends through a verticallyelongated limit pin slot |84 in the heel portion of the lever.

Since the latch |1| is maintained under constant tension by the spring |80, relaxing of the swing line I5 results in prompt return of the latch dog |12 into latching position, .the dog riding upon the upper face of the bull wheel 68 until it again registers with the latch aperture |13. Forconvenience in accommodatingthe bull wheel to use of the derrick at the left side of the truck, an auxiliary latch aperture |13"l maybe provided in the bull wheel a quarter turn removed from the aper- 40 ture |13 and adjacent the opposite end of the proximate mounting flange 69.

Immediately following unlatching of the bull wheel 68, the full pulling effect of the swing line I5I, as it continues to be reeled in, is exerted in swinging the boom 61 toward the loading position. The nature of the swing line system is such that there is a reasonably smooth transition from the slack to the boom swinging condition thereof, the inertia of the boom and the loaded bucket 30 offeritial swinging movement of the boom as the full swinging pull of the swing line |5| becomes eiective.

As the boom swings around into position over the truck body, return-swinging means, such as a spiral torsion spring |85 (Figs. 10 and 11) is loaded. This spring should be of a weight and length carefully selected to afford adequate resistancefand continuous service lfor this Particular purpose. As shown, the spring is coiled around the base portion of the stationary mast post 42 and has its inner en d fixedly secured to the mast while its outer end is secured to one `of the boom supporting brackets 69. The arrangement spring |85 functions to return the booin to'its overside position.

As a safety measure,|swinging movement of 'the boom 61 in either direction ispositively lim- `of the dog |86 with the stop |88 and overside swlngingmovement is limited by engagement of the. dog with the stop |89. While the latch |1| normally stops and retains 1the boom at about 45 rearwardly in the overside position, manual withholding or neutralizing of the latch will permit full or perpendicular overside swinging of the boom to the limit of the stop |89, if desired. An alternative land |81 may be formed on the bull wheel 68 for attachment of the dog |86 upon reversal of the boom for use at the opposite side of the truck.

Should the truck accidentally completely overrun'in reverse incidental to hoisting, dangerous tension might be created in the swing line cable |5| after the boom has reached the extreme limit of its inward swing as determined by the stop |88. Therefore, an overrun safety release device is provided..preferablyryin association with the slack takeup cable |62 (Figs. 4, 5 and 6), which in such event will allow the swing line cable '|5| to fall slack. To 'this end the slack takeup cable |62 at all times, even after being arrestedin its differential yielding function, maintains a substantial reserve loop in the swing line |5| (see dot-dash position of Fig. Then if the swing line becomes over-taut, the slack takeup cable |62 is automatically released from the counterweight |65, allowing both the counterweight and the pulley block 6| to drop with an audible warning clatter, and completely relieving the swing line |5I.

In a preferred form, the automatic safety release connection for the slack takeup cable |62 with the counterweight |65 comprises a knob-like ferrule |90 which is adlustably secured to the weighted reach of the takeup cable by such means as a set screw |9| and is adapted to receive the weight of the counterweight |65 directly thereagainst. For this purpose, the counter weight |65 is formed in two parts held apart by identical spacer plates |92 dening a vertical passageway through which thesupporting ferrule |90 may pass. In assembly, a pair of anti-friction rollers |93 carried by the lower ends of a pair of convergently related straight lever arms |94, project into the path of the ferrule |90 at the lower end of the vertical passageway and engage an obtusely tapered frusto-fconical seat |95 at the upper end ofthe ferrule. The arms |94 extend upwardly and outwardly from the fer-I rule passageway under the lower foreshortened ends of the respective spacer plates |92 and bear against outwardly beveled shoulders |91 formed at such ends of the plates. In this position, the arms 94 are rockably and longitudinally shiftably supported by respective xed horizontal pins |98 which extend through short longitudinal slots |99 in the arms. Under normal conditions the arms |94 are urged longitudinally toward convergence within the vertical passage to the eX- l tent permitted by the pins |98, and tight against the respective limiting shoulders |91, by resilient means such as bar springs engaging against their upper ends. As best seen in Fig. 5, the springs 20| are preferably of angular or bell crank shape engaged within their angles by fixed transverse pins 202 closely adjacent to the respective spacer bars |92. One leg of each of the springs 20| extends outwardly and bears resiliently downwardly against an outwardly eccentric bearing heel 203 at the upper end of the associated holding arm |94. The other leg of each of the springs 20| extends upwardly adjacent an outwardly tilted upper portion 204 of the associated spacer bar which carries a tension adjusting set screw 205 directed outwardly against such leg.

In response to an excessive or overload pull on I the slack takeup cable |62, the supporting ferrule forces the retaining arms |94 axially upwardly out of its way from the normal full line position shown in Fig. 5 toward the coaxial dot-dash position, in opposition to the bar springs 20|, until, if the overload increases beyond the safety point, the ferrule rides up between the rollers |93 and passes up through the counterweight. The arms |94 are, of course, promptly snapped back into normal position. It will be observed that due to the obtuse character of theseat |95 and the direct opposing thrust of vthe bar springs 20|, resistance to release of the holding ferrule |90 will be quite substantial and not readily'overcome by ordinary jarring or occasional momentary excessive pull on the slack takeup cable |62, but a sustained overload pull will operate the safety release.

In order to permit quick and easy resetting of the safety release, the ferrule |90 is formed with a sharply tapered frusto-conical lower nose 201 which enables the` ferrule to be drawn back into the reset position past the roller ends of the arms |94 by riding of the rollers |93 onto the nose 201 whereby to cause the arms |94 to rock in the eccentric dot-dash position of Fig. 5. In

view of the gradual taper of the nose 201 and the relatively long leverage of the lower portions of the arms 94, the resistance to resetting is quite nominal. In a typical example, it requires approximately fty times as much force to eect an overload release as is required to reset the device. To facilitate resetting, a substantial hand hold length of the takeup cable |62 extends beyond the lower end of the ferrulevl90.

Proper functioning of the boom 61 requires that the mast 42 be as nearly vertical as practicable and that any slight tilting thereof from the vertical assist rather than hinder its proper functioning. That is, a slight outward tilting of the mast may be utilized in place of or in sup plement to the torsion spring |85 for normally return swinging of the boom. Where such outward tilting is excessive, however, the boom will be swung too far off balance. On the other hand, where the boom tilts inwardly or away from the side of the truck at which scraping is in progress, the over-balance will be such as to cause the boom constantly to tend to swing in over the truck and thus prevent or impede return swing. Such over-tiltingv of the mast becomes a particular problem in working upon super-elevated road curves or in other circumstances where the truck is tipped appreciably on its longitudinal axis from a normal substantially horizontal plane. Means is, therefore, provided to compensate for necessary sidewise tilting of the truck during operation by optionally adjusting the mast 42 to assume as nearly as practicable the preferred vertical working position. With particular reference to Figs. 7, 10, and 14, such verticality ad. justment means is arranged for rockably tipping the derrick base frame 55 up or down from a normal horizontal plane about the axis provided by the vrock shaft 64. To this end the shaft 63 is equipped with a pair of 'circular eccentric cams 2I0 which are removably keyed in placev as by means of set screws 2ll and slidably engageable between spaced horizontal follower ears or dogs 2l2 projecting rigidly from the inner faces of the adjacent end portions of the base frame bars -51 and 58, respectively. By rotation of the shaft 63 and thus the eccentric cams 2 I 0, the associated end of the base frame 55 can be moved from the normal horizontal full line position as shown in Fig. 14 to the up or down tilted positions shown in respective dash and dot-dash outlines, or into incremental intermediate up or down tilted positions. Since the' shaft 63 remains on a permanent axis with respect to the mounting frame bars 33 and 34, the base frame bars 51 and 68- are provided with verticalv clearance slots 2I3 l to accommodate the shaft. i

Manual locking of the cam shaft 63 may be eiected throughv the medium of a handle 2|4 (Figs. 3, '7 and 14) the grip portion of which is of `hollow tubular construction' and carries a resiiiently projected, retractible index pin 2| 5 adapted to engage within any one of a semicircular series of index holes 2H within an index plate 2|8. I'he latter is of preferably sector shape and assembled upon the shaft 63 between the shank of the handle 2|4 and-the adjacent edge of the .base frame bar 34. There the index plate is held non-rotatable by one or more interlocking blocks 2 I9 fitting within the channel of the frame bar 34. The arrangement of the handle 2I-4 relative to the eccentric. cams 2| 0 is preferably Vsuch that when the handle is in an upright position as shown in full outline in Figs. 7 and 14, the base frame 55 is located in the normal horizontal or parallel relation to the mounting frame, while when the handle ,is moved to the left as shown in Fig. 7, the adjacent end of the base frame -55 is depressed, and, conversely, when the handle is moved to the right, suchend of the base frame is raised, the mast 42 being correspondingly tilted.

Rather than to adjust the verticality of the mast, it may be desired to tiltthe mast 42 slightly in order to increase the swinging tendency of the boom 61 either to the overside position or toward the loading'position. Thismay, of course, be effected by appropriate cam adjustment to the right or to the left, respectively, by appropriate indexing of the handle 2 I4.

When the truck loader 2-5 is trimmed Ifor transit travel of thetruck 26, with the derrick collapsed or with the boom 81 at least depressed as shown in dot-dash outline of Fig. '7, the bull wheel 68 is preferably' immobilized in its'most convenient rotative position with regard to the transit position of the boom by such means as one or more immobilizing pins (not shown) which may be extended through any one of a series of pin holes 220 (Fig. 11) provided for this purpose in the bull wheel 68 with' the pins engaging some convenient part of the base frame structure. At the same time the hoisting cable "84 and the swing cable I6I vare tied down to hold the declutched winding drum Illl immobile, and the scraper dition.

When dumping the truck by rearward tilting of the truck body 21, dismantling or collapsing of the derrick structure of the loader is unneces? sary due to its" relatively light weight and compact 'construction'and the stationary-locked condition of the boom 61.

Diiiiculty has been encountered in ditching with the imperforate scoop or bucket in rocky slides containing rocks from aboutl four inch'es up to substantially larger size boulders. For handling such material efliciently, I have provided a rock fork 225 (Fig. 18) whichmay be optionally substituted for the bucket 30 and comprises a strongly reenforced open frame construction. There are, of course, many other materialhandling uses for which this fork is suitable. To attain light weight with maximum strength, the main body of the 'fork 225 is constructed of appropriately shaped longitudinally extending tubular bars 221 which may consist of a standard type tubing. These are rigidly secured into a unitary structure by'means of tie plates 228 and a .rear frame bar structure 22.9 from which extends rearwardly a handle 23|) held rigid by a yoke 23|. 221 form sockets within which are inserted forwardly projecting hardened steel tines 232 (Fig. 19) secured in place by means such as soft rivets 233 and rearwardly abutting against base plugs 234 which may be welded in position at the proper depth within the tubes. When necessary, the tines 232 may be removed and replaced by the simple expedient of driving outthe soft rivets 233. Fixed clevices 235 may be provided at the outside of certain of the body members 221 for attachment *of the drag line to the fork.

Fo'r quick detachable connection with the hoist cable 84, the forkf 225 carries a socket body 231 ,pivotally mounted on an upstanding longitudinal of the fork when suspended from the hoistl cable.

Thev latch bar frame 240 is supported in nor- .mally spaced parallel relation to the body bars 221 by a cantilever type of supporting frame 24| which is of a substantially complementary A- shape in plan, and of substantially L-shape in side elevation, with the ends of the short leg portions thereof rigidly secured to the rear framework 229 and the sides of the yoke 23|. At its rear or wider end, the trip latch frame 240 is pivotally secured to the supporting frame 24|. At the forward end the trip latch frame is associated with a manually operable latch structure 242 which is in essential respects similar to the latch structure described inv connection with the scraper bucket 30 and normally holds the same down on the supporting frame 24| but is readily tripped for dropping the mouth of the fork down to discharge its contents. If desired, of course,

the frame structure assembly 240, 24| could be The forward ends of the body tubes used on the bucket 30 in substitute for that shown.

While I have illustrated a preferred embodiment of my invention, many modifications and substitutions may be made without departing from the spirit of the invention, and I do not wish to be limited to the precise details of construction as set forth, but desire to avail myself of all changes within the scopeof the appended claims. In the claims, the term cable" is used in a generic sense to include such equivalents as chain or rope.

Having thus described my invention, what I claim as new and desire to secure by Letters Patent of the United States is:

1. Truck loading apparatus comprising, in combination, a supporting structure adapted to be mounted upon the body of a truck and including a boom arranged to extend upwardly and outwardly beyond one side of the truck body and to swing into position overhanging the body with the top of the boom substantially spaced thereabove, a scoop device having a drag line arranged to extend forwardly therefrom, a drag bar extending laterally from one side of the truck and carried by the supporting structure, said bar having the forward endof said drag line secured adjacent its outer end, a hoisting cable secured at one end to said scoop and supported by the boom to be pulled for hoisting the scoop device, a winding drum carried by the adjacent rear wheel of the truck and arranged to rotate with the wheel when the truck is driven in one direction for winding up said hoisting cable to raise the scoop device but to rotate with the `wheel when the truck is driven in the opposite direction until the cable is unwound and thereupon to permit free rotation of the Wheel relative thereto while the 'truck is driven on to effect dragging of the scoop device along the ground through the medium of said drag line and said drag bar, and a swing cable also secured to said drum and operatively connected to said boom for swinging the boom into the overhanging position in coordination with the operation of the hoisting cable.

2. In combination in a truck loading apparatus, a supporting structure, a handling device adapted to engage, at a point outside the truck, a hoisting cable rigged on said supporting structure and attached to said handling device, a drum having said cable secured thereto and adapted to be rotated for winding the cable thereon to eiect movement of said handling device from the level at which it is loaded to a level higher than the body of the truck, and a second cable also arranged for winding upon the drum and adapted in such winding to effect movement of the elevated handling device in a generally horizontal direction over the truck body.

3. Truck loading apparatus comprising a vsupporting structure to` be mounted directly upon the truck to be loaded, a handling device adapted to receive at ground level'a load to be rdeposited in the truck, said supporting structure being rigged with a hoisting cable for elevating and lowering the handling device between the ground level and a level higher than the body of the truck, means including a cable for effecting generally horizontal movement of the handling device into position over the truck body for deposit of said load into the truck, and truck-carried `rotary structure upon which both of said cables are windable.

4. In combination in truck loading apparatus, a

supporting structure adapted to be carried by the truck to 'be loaded, a handling device adapted to receive a load at ground level to be lifted up and deposited in the truck, a, pair of cables carried by said supporting structure, one of said cables being cooperative with said handling device for lifting it fro-rn ground levelto a higher level than the truck body, the other of said cables being adapted for effecting substantially horizontal movement of the handling device over the truck after the device has been raised sufiiciently to clear above the truck body, and a winding drum mounted upon a wheel of the truck and having both of said cables secured thereto, said drum being rotatable with the wheel for winding up the cables and thereby pulling them to eiiect said lifting and shifting, respectively.

5. Truck loading apparatus as set forth in claim 4, including means comprising a reverse wound portion for maintaining a dilferential reserve in the device-shifting cable, so that for a predetermined interval in the initial windup of the cables the lifting cable will be pulled to elevate the handling device high enough to clear the truck body before the shifting cable is pulled to shift the device.

6. Truck loading apparatus comprising, in combination, a supporting structure adapted to be carried directly by the truck to be loaded, a handling device adapted to receive, outside of the truck body, a load to be delivered into the truck, means including a cable arranged to elevate the handling device from a load-receiving position below the truck body to'an elevation above the truck body, means including a cable for shifting the handling device in a generally horizontal direction into a proper position for delivery of its load into the truck, and truck-carried rotatable Wind-up structure having said cables attached 40 thereto, the relationship of the rotatable structure and the cables being such that the elevating cable is wound up to a, predetermined extent in advance of winding up of said shifting cable so as to permit elevating movement of the handling device before shifting thereof.

7. Truck loading apparatus comprising, in combination, a supporting structure adapted to be carried directly by the truck to be loaded, a handling device adapted to receive, outside of the truck body, a load to be deposited in the truck, means including a cable arranged to be pulled to elevate the handling device from a load-receiving elevation below the top of the truck body to an elevation higher than the top of the truck body, means including a cable arranged to be pulled for shifting the handling device in a generally horizontal direction into a proper position for deposit of its load into the truck, and a rotary winding drum having both of said cables attached thereto in such relationship that as the drum is rotated to wind up the elevating cable, the shifting cable is paid out during a part of the initial revolution of the drum and is thereafter wound up together with the elevating cable, the paying out of said shifting cable causing it to lag behind the pull of the elevating cable and permitting elevation of the handling device before it is shifted.

8. In combination in loading apparatus including a swingable boom, 'a load handling device, a cable for swinging said boom, a second cable for hoisting said handling device, and a rotary drum having both of said cables attached thereto and respectively making initial contact with the drum in approximately the same tangential direction at substantially diametrically opposite sides of the drum is rotated the firstv drum, so that when the y end of the cable for pulling on the cable, and

said cable will slacken oi during the ilrst part whereby to effect a lag in operation of first saidy cable with relation to the second said cable.

9. Loading apparatus as defined in claim 8, lnv cluding means for taking up the slack developed in the nrst said cable and keeping it taut during the interval in which it slackens olf. Y

10. Loading apparatus substantially as" dened in claim 8, in which the' drum has a radial opening dened by an inwardly directed easement structure to receive the end portions of both of the cables, and a. cable clamp secures the end portions of the cables inwardly of the easement structure.

1l. Loading apparatus as dened in claim 8, in which the rst said cable has a differential reserve for prolonging the lag in operation beyond that afforded by theslackening off.

12. Truck loading apparatus comprising, inl

combination, a supportingA structure adapted to be mounted directly upon the truck to be loaded, a handling device adapted to engage, outside of the truck, a load to -be deposited in the truck, means carried by said supporting structure for raising the handling device from its load-engaging position to a level higher than the truck body, said -means including a hoisting cable'and a winding drum for such cable mounted to be driven rotatably towind the cable thereon, means including a cable also arranged to be wound upon said drum for effecting generally horizontal movement of the handling devicel over the truck body after the device has been sufliciently elevated to clear thereover, said last mentioned cable having a substantial diiferential reserve with respect to the hoisting cable so that in the winding rotation of the drum the hoisting cable will operate to elevate the handling device 'before the shifting cable acts to shift the handling device, and means for taking up the differential reserve in the shifting cable arranged to yield during the winding operation of the drum to the extent of the predetermined differential whereafter the full pulling effect upon such cable resulting from windup of the cable upon the drum may become effective for shifting said device.

13. A loading apparatus as defined in claim 12, in 4which the takeup means includes a counterweight, and means for controlling its ranger of movement in the yielding of said ytakeup means, whereby to predetermine the effective extent of differential reserve of the cables.

14. 'Iruck loading apparatus as defined in claim 12, including a latch normally acting` to'lock the shifting means against shifting operaton, and means responsive to the tension, of shifting cable after said differential has been fully taken up to trip the latch.

15. In combination in loading apparatus including a supporting structure, means for actuating a load handling device including, a swinging boom structure, a swivel member carrying the base of the boom proper, a latch mechanism mounted upon said supporting structure and engageable with said swivel member to lock the boom against swinging out of a given position, an actuating cable having one end cooperating with the boom structure and being adapted to be pulled, for swinging the boom from said latched position, motivating means cooperating with the opposite vmeans intermediately engaging the cable and being movable by the cable when-pulled` toa predetermined extent to release the latch so that thel cable may thenswing the boom.

16. loading apparatus. including a supporting structure, a load-handling device, a pair of cables rigged onsaid supporting structure for actuating said device, means for actuating said cables simultaneously, one of said' cables having a differential reserve, takeup means including a cable and a counterweight structure for yieldably taking up said differential reserve to avoid slackness in said one cable, and safety means effecting a connection between said takeup cable and'said counterweight structure constructed and arranged to release the takeup cable to fall slack when placed under overload tension by said onev cable.

Y 17. In truck mounted loading apparatus of the g character described, a material handling device,

motivating means for saidmaterial handling device including,r a cable anda winding drum for said cable, and means for mounting said drum upon a wheel of the truck comprising a ilange member having one end iixedly secured to and rotatable with the wheel and a second member removably connected to the other end of said wheel mounted member, the drum being rotatably mounted upon said second member.

18. Loading apparatus for actuating a material handling device, comprising means for actuating said handling-device including a cable, said cable having, intermediate its ends, a substantial reserve loop, safety means including a slacktakeup structure normally maintaining the cable operatively taut and operative when the cableis placed lunder overload tension to yield said re- Y serve loop and allow the cable to fall slack.

19. In combination in loading apparatus including a material handling device adapted to be dragged along the ground for scooping up material to be loaded into the truck, hoisting structure, including certain rigid components and arranged to be carried by the truck for raising and lowering the scooping device between scooping and truck loading positions, a drag line attached rto said scooping device, a drag bar arranged to extend outwardly beyond the side of the truck for dragging the scooping device through the medium of said drag line when the associated truck is driven in the direction of the scooping operation, said drag bar being pivotally mounted adjacent the body of the truck for vertical swinging movement, anda tie rod engagingsaid drag bar and being adjustably engageable with one of the rigid components of said hoisting structure for holding the drag bar in various selective positions of angularfadjustment relative to the side of the truck as permitted by the pivotal mounting of the drag 60 b 20. Loading apparatus as defined in claim 19, in which the tie rod is detachable to permit collapse of the drag bar into a vertically hanging out-ofthe-way position'at the side of the truck when the loading apparatus is not in use.

21. In combination in a truck-carried loader, a material handling device adapted to be dragged along the groundior' gathering material to be loaded into the truck, hoisting means for raising and lowering the handling device, a drag line attached to the handling device, a drag bar arranged to extend laterally from the truck, a tie tie rod, the connecting 1s raised to a greater distance from said meeting ends than the length of the drag line.

22. In combination in a truck-carried loader,

a handling device adapted to transfer a load from ground level into the truck, a derrick structure adapted to befmounted directly upon the body of the truck and including a boom swingable about a vertical axis, a hoisting line supported by said boom for raising and lowering said handling device, means for automatically swinging said boom between an overside position and an overhanging position relative to the truck body in coordinated sequence in the operation of said hoisting line, and means for adjusting the swinging axis of the boom with respect to the vertical to control predisposition of the boom to swing, as affected by the degree and direction of inclina- .tion of the axis from the vertical, respectively in supplement to or in opposition to the action of said boom swinging means.

23. In combination in loading apparatus adapt- I ed to be mounted upon a dump truck for use in highway maintenance work, a material handling device adapted toA be dragged along the ground or a roadside ditch to scoop up material therefrom, means for effecting a drag connection between the handling device and the truck, a-

derrick structure including a boom swingable about a vertical axis, and rigging carried by the boom for raising and lowering said handling device relative to the truck body, said derrick structure including means for adjusting the swinging axis of the boom with respect to either side of the truck in order to compensate for sidewise tilting of the truck, at super-elevated road curves or the like, and maintain the boom in a substantially balanced swingable condition.

24. In combination in apparatus of the character described, a material handling device adapted to be dragged along the ground for scooping up a load of material to be lifted into a truck, and means for lifting the handling device from the ground into a loading position over the truck,

`said handling device comprising an open framework body including forwardly opening tubular sockets and hardened tines replaceably seated within the respective sockets.

25. In combination in apparatus of the character described, a material handling device adapted to be dragged along the ground for gathering up a load of material to be lifted into a truck, including a forwardly pointing overhanging cantilever carrying frame substantially A- shape in plan and L-shape' in side elevation affording .a large forwardly opening material receiving mouth for the device, a trip bar structure of substantially complementary A-shape pivotally secured at its widest end to the wider rear portion of the carrying frame and having means at approximately the center of gravity of structure including a boom and rigging for raising and lowering the handling device, said boom being adapted to swing between a material pickup position beyond one side of the truck and a loading position over the truck body, means actuated by said rigging and automatically releasable in the operation of the apparatus for holding the boom in the material pickup position for a predetermined interval in the operating cycle, and means enabling locking of the boom in said loading position against returnto the material pickup position when the truck is in transit or is to be dumped.

27. In truck mounted loading apparatus of the character described, a material handling device, motivating means for lsaid material handling device including a cable and a winding drum for said cable,and meansvfor mounting said drum upon a wheel of the truck, said meanscomprisin'g an adapter ange tting a portion of said wheel and secured thereto for rotation therewith, said adapter flange having a connecting portion of a predetermined size, a supporting ange having said drum rotatably supported at one end thereof and having a connecting portion tting and`removably secured to the connecting portion of said adapter flange, and means selectively connecting said drum to the supporting flange for the transmission of driving force thereto from said wheel.

2.8. In combination with a truck carried loader, a handling device adapted to transfer a load from ground level into the truck, a derrick structure adapted to be mounted directly upon the body of the truck and including a boom swingable about a vertical axis, said derrick structure also including a mounting from and a base frame carried by the mounting frame, a hoisting line supported by said boom for raising and lowering said handling device, means for automatically swinging said boom between an over-side position and an overhanging position relative to the truck body in coordinated sequence in the operation of said hoisting line, and means for adjusting the swinging axis of the boom with respect to thevertical to control predisposition of the boom to swing, as affected by the degree and direction of inclination of the axis from the vertical, relatively in supplement to or in opposition to the action of the boom-swinging means, said adjusting means comprising a mechanism for tilting the base frame relative to the mounting frame.

ROBERT C. SHOEMAKER. 

